Radial piston hydraulic device

Abstract

The application provides a radial plunger hydraulic device and relates to the technical field of hydraulic transmission. The radial plunger hydraulic device comprises a flow distribution part connected with an eccentric main shaft, the flow distribution part comprises a first high-pressure flow distribution window, a first low-pressure flow distribution window, a second high-pressure flow distribution window, a second low-pressure flow distribution window, a high-pressure oil hole and a low-pressure oil hole; the flow distribution part is adapted to rotate with the eccentric main shaft and is configured to be capable of controlling the first high-pressure flow distribution window and the first low-pressure flow distribution window to be connected with the first control oil path in advance / delayed or controlling the second high-pressure flow distribution window and the second low-pressure flow distribution window to be connected with the second control oil path in advance / delayed, so that the hydraulic control one-way valve is closed when the two-way plug-in valve is opened or the hydraulic control one-way valve is opened when the two-way plug-in valve is closed. Through the scheme, the volumetric efficiency of the radial plunger hydraulic device can be improved and the impact and vibration can be relieved.

Description

Technical Field

[0001] This invention belongs to the field of hydraulic transmission technology, and more specifically, relates to a radial piston hydraulic device. Background Technology

[0002] Radial piston hydraulic devices are extremely important actuators in hydraulic systems, widely used in engineering machinery, military machinery, construction machinery, mining machinery and other fields. The main flow distribution methods of radial piston hydraulic devices are divided into three types: shaft flow distribution, end face flow distribution, and valve flow distribution. In the valve flow distribution technology with pilot pressure control, the response of the valve core directly affects the performance of the radial piston hydraulic device.

[0003] In a radial piston hydraulic system with pilot pressure control valve distribution, one piston chamber connects to two seat valves: one for oil inlet and one for oil outlet. Ideally, when one valve is open, the other is closed. However, due to the delay in valve core opening and closing, both valve cores may open simultaneously during switching. This stage generates significant oil leakage and impact vibration, affecting the volumetric efficiency and operational stability of the radial piston hydraulic system. Existing vibration reduction and noise reduction methods in axial piston hydraulic systems mainly fall into two categories: reducing the intensity of the excitation source and blocking its propagation. Methods for reducing the intensity of the excitation source include creating damping grooves (holes), using check valves, adjusting misalignment angles, rotation angles, closed volumes, staggered angles, and pre-compression volumes. These techniques increase the pressure of the low-pressure oil within the piston, reducing the pressure difference between the oil in the piston chamber and the outlet oil. This prevents the pressure difference from becoming too large when the oil in the piston chamber is connected to the outlet load, thus achieving vibration reduction and noise reduction. Current technologies all involve the distribution window of the distribution device being directly connected to the plunger cavity. However, radial plunger hydraulic devices that use pilot pressure control valves for distribution are two-stage distribution devices, with the main stage being distribution via a seat valve. Thanks to the good sealing performance of the seat valve, the distribution window of the distribution device only controls the opening and closing of the seat valve and is not connected to the plunger cavity. Therefore, the above methods are not suitable for vibration reduction and noise reduction of radial plunger hydraulic devices that use pilot pressure control valves for distribution. Summary of the Invention

[0004] This invention discloses a radial piston hydraulic device, which aims to improve the existing radial piston hydraulic device. Due to the delay in valve core opening and closing, the two valve cores may open simultaneously during the flow distribution state switching, resulting in large oil leakage and impact vibration, which affects the volumetric efficiency and operational stability of the radial piston hydraulic device.

[0005] The present invention adopts the following solution:

[0006] This invention provides a radial piston hydraulic device, including an eccentric spindle, a manifold, a two-way cartridge valve, and a hydraulically controlled check valve. The manifold includes a first control oil circuit and a second control oil circuit. The first control oil circuit is connected to the two-way cartridge valve, which is configured to be closed under high pressure and open under low pressure. The second control oil circuit is connected to the hydraulically controlled check valve, which is configured to be open under high pressure and closed under low pressure. The device also includes a distribution component connected to the eccentric spindle, comprising a first high-pressure distribution window, a first low-pressure distribution window, a second high-pressure distribution window, a second low-pressure distribution window, a high-pressure oil port, and a low-pressure oil port.

[0007] The first high-pressure distribution window and the first low-pressure distribution window are alternately connected to the control chamber of the two-way cartridge valve through the first control oil circuit, and the high-pressure oil hole is connected to the high-pressure main port, the first high-pressure distribution window, and the second high-pressure distribution window;

[0008] The second high-pressure distribution window and the second low-pressure distribution window are alternately connected to the control chamber of the hydraulic check valve through the second control oil circuit. The low-pressure oil hole is connected to the low-pressure main port, the first low-pressure distribution window, and the second low-pressure distribution window.

[0009] The flow distribution component is adapted to rotate with the eccentric main shaft and is configured to connect the first control oil circuit in advance / delay by controlling the first high-pressure flow distribution window and the first low-pressure flow distribution window, or to connect the second control oil circuit in advance / delay by controlling the second high-pressure flow distribution window and the second low-pressure flow distribution window, so that when the two-way cartridge valve is open, the hydraulic control check valve is closed, or when the two-way cartridge valve is closed, the hydraulic control check valve is open.

[0010] Furthermore, the distribution component is a distribution shaft that is connected to the eccentric main shaft drive. The distribution shaft also includes a high-pressure annular groove and a low-pressure annular groove. The first high-pressure distribution window, the first low-pressure distribution window, the second high-pressure distribution window, and the second low-pressure distribution window are arranged around the distribution shaft. The high-pressure annular groove is connected to the high-pressure main port and communicates with the high-pressure oil hole. The low-pressure annular groove is connected to the low-pressure main port and communicates with the low-pressure oil hole.

[0011] Furthermore, the first high-voltage distribution window, the first low-voltage distribution window, the second high-voltage distribution window, and the second low-voltage distribution window are arc-shaped, and the span angle of the first high-voltage distribution window is defined as β1, the span angle of the first low-voltage distribution window is defined as γ1, the span angle of the second high-voltage distribution window is defined as β2, and the span angle of the second low-voltage distribution window is defined as γ2.

[0012] Furthermore, β1 > γ1, β2 < γ2.

[0013] Furthermore, β1 = γ1, and β2 < γ2.

[0014] Furthermore, there is a deflection angle θ between the two-way cartridge valve and the first high-pressure distribution window. E The deflection angle θ E The formula for calculation is:

[0015] θ E =6nt1;

[0016]

[0017]

[0018] Where n is the rotational speed of the distribution shaft, t1 is the response time of the two-way cartridge valve, Q is the inlet flow rate, V is the discharge rate, and η is the displacement. v It is the volumetric efficiency, x1 is the spool stroke of the two-way cartridge valve, q1 is the inlet flow rate of the two-way cartridge valve, and d1 is the diameter of the two-way cartridge valve.

[0019] Meanwhile, there is a deflection angle θ between the hydraulically controlled check valve and the second low-pressure distribution window. Y The deflection angle θ Y The formula for calculation is:

[0020] θ Y =6nt2;

[0021]

[0022]

[0023] Where n is the rotational speed of the distribution shaft, t2 is the response time of the hydraulic check valve, Q is the inlet flow rate, V is the discharge capacity, and η is the displacement. v x2 is the volumetric efficiency, q2 is the stroke of the hydraulic check valve spool, d2 is the inlet flow rate of the hydraulic check valve spool, and d2 is the diameter of the hydraulic check valve spool.

[0024] Furthermore, β1 = γ1 + θ E γ2=β2+θ Y .

[0025] Furthermore, there exists a turning angle α between the first high-voltage distribution window and the first low-voltage distribution window, and between the second high-voltage distribution window and the second low-voltage distribution window, and the following conditions are met: Where D1 is the diameter of the distribution shaft and D2 is the pipe diameter of the first or second control oil circuit.

[0026] Furthermore, the line connecting the first control oil circuit and the second control oil circuit on the distribution shaft is parallel to the central axis of the distribution shaft.

[0027] Furthermore, the distribution component is a distribution plate connected to the eccentric spindle drive. The distribution plate includes a first set of waist-shaped grooves for connection to the two-way cartridge valve and a second set of waist-shaped grooves for connection to the hydraulic check valve. The first set of waist-shaped grooves includes a first high-pressure distribution window and a first low-pressure distribution window, and the second set of waist-shaped grooves includes a second high-pressure distribution window and a second low-pressure distribution window.

[0028] Beneficial effects:

[0029] In this invention, the distribution shaft is a two-stage distribution shaft. The main oil circuit consists of two seat valves corresponding to the plunger. The pilot-stage distribution shaft controls the control chambers of the two-way cartridge valve and the hydraulically controlled check valve, thereby controlling their opening and closing. The main oil circuit and the pilot oil circuit are separated. The pilot oil circuit has a low flow rate, which reduces oil leakage. Compared with a single-stage distribution shaft, it has higher volumetric efficiency and output torque. By adjusting the span angle and deflection angle of the high and low pressure windows of the distribution element, the opening and closing timing of the two-way cartridge valve and the hydraulically controlled check valve can be controlled, avoiding the phenomenon of severe oil leakage caused by the simultaneous opening of the two-way cartridge valve and the hydraulically controlled check valve. This can greatly improve the volumetric efficiency of the radial plunger hydraulic device and alleviate impact vibration. Attached Figure Description

[0030] Figure 1 This is an isometric schematic diagram of a device for reducing the pressure shock of a pilot pressure-controlled hydraulic pump motor according to an embodiment of the present invention.

[0031] Figure 2 This is an axial cross-sectional schematic diagram of a radial plunger hydraulic device for pilot pressure control valve flow distribution according to an embodiment of the present invention.

[0032] Figure 3 for Figure 2 A magnified view of a portion of the image.

[0033] Figure 4 This is an axial cross-sectional schematic diagram of a device for reducing the pressure impact of a pilot pressure control hydraulic pump motor according to an embodiment of the present invention.

[0034] Figure 5 for Figure 4 A schematic diagram of the AA section.

[0035] Figure 6 Figure 4 BB cross-sectional diagram.

[0036] Figure 7 This is a schematic diagram illustrating the working principle of a radial plunger hydraulic device for pilot pressure control valve flow distribution according to an embodiment of the present invention.

[0037] Figure 8This is a schematic diagram illustrating the working principle of the device for reducing pilot pressure control and distribution hydraulic pump motor pressure shock according to Embodiment 1 of the present invention.

[0038] Figure 9 This is a schematic diagram showing the relationship between the valve core displacement and time in the radial plunger hydraulic device with pilot pressure control valve distribution according to Embodiment 1 of the present invention.

[0039] Figure 10 This is a schematic diagram illustrating the working principle of the device for reducing pilot pressure control and distribution hydraulic pump motor pressure shock according to Embodiment 2 of the present invention.

[0040] Figure 11 This is a schematic diagram showing the relationship between the valve core displacement and time in the radial plunger hydraulic device with pilot pressure control valve distribution according to Embodiment 2 of the present invention.

[0041] Figure 12 This is a schematic diagram illustrating the working principle of the device for reducing pilot pressure control and distribution hydraulic pump motor pressure shock according to Embodiment 3 of the present invention.

[0042] Reference numerals in the attached drawings: 1. Eccentric spindle; 2. Manifold; 3. Distribution shaft; 4. Hydraulic check valve; 5. Two-way cartridge valve; 6. First low-pressure distribution window; 7. High-pressure annular groove; 8. Second low-pressure distribution window; 9. Sealing device; 10. Bearing; 11. Second high-pressure distribution window; 12. Second control oil circuit; 13. Low-pressure annular groove; 14. First control oil circuit; 15. First high-pressure distribution window; 16. Low-pressure oil hole; 17. High-pressure oil hole. Detailed Implementation

[0043] Example 1

[0044] Combination Figure 1 As for Figure 4 As shown in the figure, this embodiment of the present invention provides a radial piston hydraulic device, including an eccentric spindle 1, a manifold 2, a two-way cartridge valve 5, and a hydraulically controlled check valve 4. The manifold 2 includes a first control oil circuit 14 and a second control oil circuit 12. The first control oil circuit 14 is connected to the two-way cartridge valve 5, which is configured to be closed under high pressure and open under low pressure. The second control oil circuit 12 is connected to the hydraulically controlled check valve 4, which is configured to be open under high pressure and closed under low pressure. The device also includes a distribution component connected to the eccentric spindle 1, comprising a first high-pressure distribution window 15, a first low-pressure distribution window 6, a second high-pressure distribution window 11, a second low-pressure distribution window 8, a high-pressure oil port 17, and a low-pressure oil port 16.

[0045] The first high-pressure distribution window 15 and the first low-pressure distribution window 6 are alternately connected to the control chamber of the two-way cartridge valve 5 through the first control oil circuit 14, and the high-pressure oil hole 17 is connected to the high-pressure main port, the first high-pressure distribution window 15, and the second high-pressure distribution window 11.

[0046] The second high-pressure distribution window 11 and the second low-pressure distribution window 8 are alternately connected to the control chamber of the hydraulic check valve 4 through the second control oil circuit 12. The low-pressure oil hole 16 is connected to the low-pressure main port, the first low-pressure distribution window 6, and the second low-pressure distribution window 8.

[0047] The flow distribution component is adapted to rotate with the eccentric main shaft 1 and is configured to connect the first control oil circuit 14 in advance / delay by controlling the first high-pressure flow distribution window 15 and the first low-pressure flow distribution window 6, or to connect the second control oil circuit 12 in advance / delay by controlling the second high-pressure flow distribution window 11 and the second low-pressure flow distribution window 8, so that when the two-way cartridge valve 5 is open, the hydraulic control check valve 4 is closed, or when the two-way cartridge valve 5 is closed, the hydraulic control check valve 4 is open.

[0048] In this embodiment, the radial plunger hydraulic device includes a housing, a manifold 2, and a plunger assembly. The plunger assembly is installed in the plunger cavity of the housing. The manifold 2 is provided with a first control oil circuit 14 and a second control oil circuit 12. The structure of the manifold 2, the plunger cavity, and the housing can be referenced to the four-quadrant radial plunger hydraulic device and its working method with dual valve distribution, as disclosed in CN116378892B. In this embodiment, an example is given where the housing has five plunger cavities. Each plunger cavity is connected to a two-way cartridge valve 5 and a hydraulically controlled check valve 4. The two-way cartridge valve 5 is connected to the distribution element through the first control oil circuit 14, and the hydraulically controlled check valve 4 is connected to the distribution element through the second control oil circuit 12. The two-way cartridge valve 5 is configured to be closed under high pressure and open under low pressure; the hydraulically controlled check valve 4 is configured to be open under high pressure and closed under low pressure; the structure of the two-way cartridge valve 5 and the hydraulically controlled check valve 4 can also refer to the dual-valve flow distribution four-quadrant radial piston hydraulic device and its working method disclosed in CN116378892B.

[0049] In this embodiment, the eccentric spindle 1 can drive the distribution component to rotate, thereby controlling the rotation of the distribution component to switch between high pressure and low pressure between the first control oil circuit 14 and the second control oil circuit 12, and thus controlling the opening and closing of the two-way cartridge valve 5 and the hydraulic control check valve 4.

[0050] Combination Figures 1 to 6As shown, in this embodiment, the distribution component is described using the distribution shaft 3 as an example. One end of the distribution shaft 3 is inserted into the eccentric main shaft 1, and the other end is fixed by the bearing 10. The distribution shaft 3 has four distribution windows of different arc lengths, a high-pressure oil hole 17, a low-pressure oil hole 16, a high-pressure annular groove 7 communicating with the high-pressure main port, and a low-pressure annular groove 13 communicating with the low-pressure main port. The distribution windows are respectively a first high-pressure distribution window 15, a first low-pressure distribution window 6, a second high-pressure distribution window 11, and a second low-pressure distribution window 8. The first high-pressure distribution window 15 and the first low-pressure distribution window 6 are alternately connected to the control chamber of the two-way cartridge valve 5 through the first control oil circuit 14. The second high-pressure distribution window 11 and the second low-pressure distribution window 8 are alternately connected to the control chamber of the hydraulic check valve 4 via the second control oil circuit 12. The high-pressure annular groove 7 is connected to the high-pressure main port, and the low-pressure annular groove 13 is connected to the low-pressure main port. The high-pressure oil hole 17 is connected to the first high-pressure distribution window 15, the high-pressure annular groove 7, and the second high-pressure distribution window 11, and the low-pressure oil hole 16 is connected to the first low-pressure distribution window 6, the low-pressure annular groove 13, and the second low-pressure distribution window 8. Here, the distribution windows, the high-pressure annular groove 7, and the low-pressure annular groove 13 are separated by a sealing device 9 to prevent oil leakage.

[0051] Combination Figure 5 and Figure 6 As shown, the first high-pressure distribution window 15, the first low-pressure distribution window 6, the second high-pressure distribution window 11, and the second low-pressure distribution window 8 are arc-shaped. The span angle of the first high-pressure distribution window 15 is defined as β1, the span angle of the first low-pressure distribution window 6 as γ1, the span angle of the second high-pressure distribution window 11 as β2, and the span angle of the second low-pressure distribution window 8 as γ2. Here, the first high-pressure distribution window 15 and the first low-pressure distribution window 6 are separated by a solid part, and the second high-pressure distribution window 11 and the second low-pressure distribution window 8 are also separated by a solid part. By setting different values ​​of β1 and γ1, the connection timing between the first high-pressure distribution window 15 and the first low-pressure distribution window 6 and the first control oil circuit 14 during rotation is controlled. At the same time, by setting different values ​​of β2 and γ2, the connection timing between the second high-pressure distribution window 11 and the second low-pressure distribution window 8 and the first control oil circuit 14 during rotation is controlled. In this embodiment, the line connecting the first control oil circuit 14 and the second control oil circuit 12 on the distribution shaft 3 is parallel to the central axis of the distribution shaft 3. Therefore, the span angle and deflection angle between the first high-pressure distribution window 15 and the first low-pressure distribution window 6 or the second high-pressure distribution window 11 and the second low-pressure distribution window 8 are controlled to adjust the opening and closing timing of the two-way cartridge valve 5 and the first control oil circuit 14, as well as the opening and closing timing of the hydraulic control check valve 4 and the second control oil circuit 12, so that the two are staggered in their opening timing, preventing the two-way cartridge valve 5 and the hydraulic control check valve 4 from opening at the same time and causing oil leakage.

[0052] Here, it is defined that there is a deflection angle θ between the two-way cartridge valve 5 and the first high-pressure distribution window 15. E Then the deflection angle θ E The formula for calculation is:

[0053] θ E =6nt1;

[0054]

[0055]

[0056] Where n is the rotational speed of the distribution shaft 3, t1 is the response time of the two-way cartridge valve 5, Q is the inlet flow rate, V is the discharge rate, and η is the displacement. v It is the volumetric efficiency, x1 is the stroke of the 5th valve core of the two-way cartridge valve, q1 is the inlet flow rate of the 5th valve core of the two-way cartridge valve, and d1 is the diameter of the 5th valve core of the two-way cartridge valve.

[0057] Simultaneously, a deflection angle θ is defined between the hydraulically controlled check valve 4 and the second low-pressure distribution window 8. Y The deflection angle θ Y The formula for calculation is:

[0058] θ Y =6nt2;

[0059]

[0060]

[0061] Where n is the rotational speed of the distribution shaft 3, t2 is the response time of the hydraulic check valve 4, Q is the inlet flow rate, V is the discharge rate, and η is the displacement. v x2 is the volumetric efficiency, q2 is the stroke of the hydraulic check valve 4 spool, d2 is the inlet flow rate of the hydraulic check valve 4 spool, and d2 is the diameter of the hydraulic check valve 4 spool.

[0062] Here, through the aforementioned θ Y θ E The calculated values ​​are used to control the span angle of the first high-voltage distribution window 15, the first low-voltage distribution window 6, the second high-voltage distribution window 11, and the second low-voltage distribution window 8. Specifically, there is a turning angle α between the first high-voltage distribution window 15 and the first low-voltage distribution window 6, and between the second high-voltage distribution window 11 and the second low-voltage distribution window 8, and the following conditions are met: Where D1 is the diameter of the distribution shaft 3, and D2 is the pipe diameter of the first control oil circuit 14 or the second control oil circuit 12. In this embodiment, β1 = γ1 + θ E γ2=β2+θ Y Here θ EIt is the deviation angle θ of the solid portion of the first control oil circuit 14 relative to the first high-pressure distribution window 15 and the first low-pressure distribution window 6; Y It is the deviation angle of the second control oil circuit 12 relative to the solid portion between the second high-pressure distribution window 11 and the second low-pressure distribution window 8. In the following embodiment, θ is used as... E The value is 6°, and the θ is... Y Let's take 10° as an example for explanation.

[0063] Figure 7 This is a schematic diagram of the radial piston hydraulic device flow distribution principle via a pilot pressure control valve in this embodiment (without adjusting the span angle and deflection angle). Currently, it is in motor operating mode. Piston chambers I, II, III, IV, and V are respectively connected to a two-way cartridge valve 5 and a pilot-operated check valve 4. The two-way cartridge valve 5 is used for oil inlet to the piston chamber, and the pilot-operated check valve 4 is used for oil outlet to the piston chamber. The opening and closing of the two valves are controlled by the pilot stage distribution shaft 3. Figure 7 Based on the current spatial positions of the plungers and distribution shaft 3, plungers I and II are in the oil outlet state, plungers III and IV are in the oil inlet state, and plunger V is in the bottom position. As the distribution shaft 3 and eccentric main shaft 1 rotate clockwise together, the control chambers of both valves simultaneously enter a high-pressure state. According to the characteristic that the two-way cartridge valve 5 closes under high pressure and the hydraulic check valve 4 opens under high pressure, the two-way cartridge valve 5 (E) begins to close, and the hydraulic check valve 4 (G) begins to open. Plunger V changes from the oil inlet state to the oil outlet state after passing through the bottom position. Without adjusting the span angle and deflection angle of the distribution window, the valve core displacement of the two valves corresponding to plunger V changes over time as follows: Figure 9 In the upper part, due to the delay in the opening and closing of the two valves, there will be a stage where both valve cores open simultaneously, such as... Figure 9 In the overlapping part of the upper part of the diagram, this stage will produce some oil leakage and impact vibration, resulting in low volumetric efficiency and large fluctuations in output torque.

[0064] like Figure 8 As shown, by adjusting the span angle and deflection angle of the high and low pressure distribution windows of the distribution shaft 3, the span angle β1 of the first high pressure distribution window 15 is slightly larger than the span angle γ1 of the first low pressure distribution window 6, and the span angle β2 of the second high pressure distribution window 11 is slightly smaller than the span angle γ2 of the second low pressure distribution window 8. When the distribution shaft 3 rotates clockwise, the control chamber of the two-way cartridge valve 5 is θ ahead of the control chamber of the hydraulic check valve 4. E =6° enters the high-pressure distribution window, the control chamber of the hydraulic check valve 4 is advanced by θ Y =10° entering the low-pressure distribution window, the effect obtained corresponds to Figure 9In the lower part, based on the characteristics that the two-way cartridge valve 5 is open under low pressure and the hydraulic control check valve 4 is open under high pressure, the two-way cartridge valve 5 closes in advance, and the hydraulic control check valve 4 also closes in advance. The hydraulic control check valve 4 will open again after the two-way cartridge valve 5 is completely closed, and the two-way cartridge valve 5 will open again after the hydraulic control check valve 4 is completely closed. This avoids the phenomenon of serious oil leakage caused by the simultaneous opening of the two valves, and greatly improves the volumetric efficiency of the radial piston hydraulic device and alleviates impact vibration.

[0065] Example 2

[0066] like Figure 10 As shown, in this embodiment, the span angle and deflection angle of the high and low pressure distribution windows of the distribution shaft 3 are adjusted so that the span angle β1 of the first high pressure distribution window 15 is equal to the span angle γ1 of the first low pressure distribution window 6, and the span angle β2 of the second high pressure distribution window 11 is slightly smaller than the span angle γ2 of the second low pressure distribution window 8. When the distribution shaft 3 rotates clockwise, the control chamber of the hydraulic check valve 4 is delayed by θ compared to the control chamber of the two-way cartridge valve 5. E =6° Entering the high-pressure distribution window, the control chamber of the hydraulic check valve 4 is also θ° ahead of the control chamber of the two-way cartridge valve 5. E =10° entering the low-pressure distribution window, the effect obtained corresponds to Figure 11 In the lower part, based on the characteristics that the two-way cartridge valve 5 is open under low pressure and the hydraulic control check valve 4 is open under high pressure, the hydraulic control check valve 4 is delayed in opening and will close in advance. In this way, the two-way cartridge valve 5 closes before the hydraulic control check valve 4 opens, and the two-way cartridge valve 5 opens after the hydraulic control check valve 4 is completely closed. This avoids the phenomenon of serious oil leakage caused by the simultaneous opening of the two valves, and greatly improves the volumetric efficiency of the radial piston hydraulic device and reduces impact vibration.

[0067] Example 3

[0068] like Figure 12As shown, in this embodiment, the flow distribution component is a flow distribution plate that is drivenly connected to the eccentric main shaft 1. The flow distribution plate includes a first set of waist-shaped grooves connected to the two-way cartridge valve 5 and a second set of waist-shaped grooves for connecting to the hydraulic control check valve. The first set of waist-shaped grooves includes a first high-pressure flow distribution window 15 and a first low-pressure flow distribution window 6, and the second set of waist-shaped grooves includes a second high-pressure flow distribution window 11 and a second low-pressure flow distribution window 8. The first set of waist-shaped grooves controls the opening and closing of the two-way cartridge valve 5, and the second set of waist-shaped grooves controls the opening and closing of the hydraulically controlled check valve 4. Adjusting the lengths of the two sets of waist-shaped grooves ensures that the first high-pressure distribution window 15 of the first set of waist-shaped grooves is slightly longer than the first low-pressure distribution window 6, and the second high-pressure distribution window 11 of the second set of waist-shaped grooves is slightly shorter than the second low-pressure distribution window 8. As the distribution plate rotates clockwise with the eccentric main shaft 1, the control chamber of the hydraulically controlled check valve 4 enters the high-pressure distribution window 6° later than the control chamber of the two-way cartridge valve 5, and the control chamber of the hydraulically controlled check valve 4 enters the low-pressure distribution window 10° earlier than the control chamber of the two-way cartridge valve 5. The resulting effect corresponds to... Figure 9 In the lower part, based on the characteristics that the two-way cartridge valve 5 is open under low pressure and the hydraulic control check valve 4 is open under high pressure, the two-way cartridge valve 5 closes in advance, the hydraulic control check valve 4 closes in advance, and the hydraulic control check valve 4 opens after the two-way cartridge valve 5 is completely closed. The two-way cartridge valve 5 opens after the hydraulic control check valve 4 is completely closed. This avoids the phenomenon of serious oil leakage caused by the simultaneous opening of the two valves, and greatly improves the volumetric efficiency of the radial piston hydraulic device and reduces impact vibration.

[0069] It should be understood that the above are merely preferred embodiments of the present invention, and the scope of protection of the present invention is not limited to the above embodiments. All technical solutions that fall within the scope of the present invention are within the scope of protection of the present invention.

[0070] The accompanying drawings used in the above description of the embodiments only illustrate certain embodiments of the present invention and should not be regarded as a limitation of the scope. For those skilled in the art, other related drawings can be obtained from these drawings without creative effort.

Claims

1. A radial piston hydraulic device, comprising an eccentric spindle, a manifold, a two-way cartridge valve, and a pilot-operated check valve, wherein, The manifold includes a first control oil circuit and a second control oil circuit. The first control oil circuit is connected to the two-way cartridge valve, which is configured to close under high pressure and open under low pressure. The second control oil circuit is connected to a hydraulically controlled check valve, which is configured to open under high pressure and close under low pressure. The system is characterized by further including a distribution component connected to the eccentric spindle. The distribution component includes a first high-pressure distribution window, a first low-pressure distribution window, a second high-pressure distribution window, a second low-pressure distribution window, a high-pressure oil port, and a low-pressure oil port. The first high-pressure distribution window and the first low-pressure distribution window are alternately connected to the control chamber of the two-way cartridge valve through the first control oil circuit, and the high-pressure oil hole is connected to the high-pressure main port, the first high-pressure distribution window, and the second high-pressure distribution window; The second high-pressure distribution window and the second low-pressure distribution window are alternately connected to the control chamber of the hydraulic check valve through the second control oil circuit. The low-pressure oil hole is connected to the low-pressure main port, the first low-pressure distribution window, and the second low-pressure distribution window. The flow distribution component is adapted to rotate with the eccentric main shaft and is configured to connect the first control oil circuit in advance / delay by controlling the first high-pressure flow distribution window and the first low-pressure flow distribution window, or to connect the second control oil circuit in advance / delay by controlling the second high-pressure flow distribution window and the second low-pressure flow distribution window, so that when the two-way cartridge valve is open, the hydraulic control check valve is closed, or when the two-way cartridge valve is closed, the hydraulic control check valve is open; The first high-voltage distribution window, the first low-voltage distribution window, the second high-voltage distribution window, and the second low-voltage distribution window are all arc-shaped, and the span angle of the first high-voltage distribution window is defined as follows: The first low-pressure distribution window span angle is The second high-voltage distribution window span angle is The second low-pressure distribution window span angle There is a deflection angle between the two-way cartridge valve and the first high-pressure distribution window. The deflection angle The formula for calculation is: ； ； ； in, The rotational speed of the distribution shaft, The response time of a two-way cartridge valve. It's inbound traffic. It is displacement, It's volumetric efficiency. It is a two-way cartridge valve spool stroke, It is the inlet flow rate of the two-way cartridge valve core. It is the diameter of the spool of a two-way cartridge valve; Meanwhile, there is a deflection angle between the hydraulically controlled check valve and the second low-pressure distribution window. The deflection angle The formula for calculation is: ; ; ; in, The rotational speed of the distribution shaft, The response time of the hydraulic check valve. It's inbound traffic. It is displacement, It's volumetric efficiency. It is the valve core stroke of the hydraulic control check valve. It is the inlet flow rate of the hydraulic check valve core. It is the diameter of the valve core of the hydraulic check valve; among which, = + ; = + .

2. The radial piston hydraulic device according to claim 1, characterized in that, The distribution component is a distribution shaft that is connected to the eccentric main shaft drive. The distribution shaft also includes a high-pressure annular groove and a low-pressure annular groove. The first high-pressure distribution window, the first low-pressure distribution window, the second high-pressure distribution window, and the second low-pressure distribution window are arranged around the distribution shaft. The high-pressure annular groove is connected to the high-pressure main port and communicates with the high-pressure oil hole. The low-pressure annular groove is connected to the low-pressure main port and communicates with the low-pressure oil hole.

3. The radial plunger hydraulic device according to claim 1, characterized in that, ＞ ， ＜ 。 4. The radial plunger hydraulic device according to claim 1, characterized in that, ,and < .

5. The radial plunger hydraulic device according to claim 2, characterized in that, There are angles between the first high-voltage distribution window and the first low-voltage distribution window, as well as between the second high-voltage distribution window and the second low-voltage distribution window. And satisfy ,in, It is the diameter of the distribution shaft. It refers to the pipe diameter of the first or second control oil circuit.

6. The radial plunger hydraulic device according to claim 2, characterized in that, The line connecting the first control oil circuit and the second control oil circuit on the distribution shaft is parallel to the central axis of the distribution shaft.

7. The radial plunger hydraulic device according to claim 1, characterized in that, The distribution component is a distribution plate that is connected to the eccentric spindle drive. The distribution plate includes a first set of waist-shaped grooves for connecting to the two-way cartridge valve and a second set of waist-shaped grooves for connecting to the hydraulic check valve. The first set of waist-shaped grooves includes a first high-pressure distribution window and a first low-pressure distribution window, and the second set of waist-shaped grooves includes a second high-pressure distribution window and a second low-pressure distribution window.

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